WO2011001155A2 - Train d'engrenages - Google Patents

Train d'engrenages Download PDF

Info

Publication number
WO2011001155A2
WO2011001155A2 PCT/GB2010/001284 GB2010001284W WO2011001155A2 WO 2011001155 A2 WO2011001155 A2 WO 2011001155A2 GB 2010001284 W GB2010001284 W GB 2010001284W WO 2011001155 A2 WO2011001155 A2 WO 2011001155A2
Authority
WO
WIPO (PCT)
Prior art keywords
gears
gear
shaft
input
lay
Prior art date
Application number
PCT/GB2010/001284
Other languages
English (en)
Other versions
WO2011001155A8 (fr
WO2011001155A3 (fr
Inventor
Changxiu Zhou
Original Assignee
Smart Manufacturing Technology Limited Et Al
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Smart Manufacturing Technology Limited Et Al filed Critical Smart Manufacturing Technology Limited Et Al
Priority to GB1121893.0A priority Critical patent/GB2485290B/en
Priority to CN201080029896.6A priority patent/CN102667237B/zh
Publication of WO2011001155A2 publication Critical patent/WO2011001155A2/fr
Publication of WO2011001155A8 publication Critical patent/WO2011001155A8/fr
Publication of WO2011001155A3 publication Critical patent/WO2011001155A3/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
    • F16H1/22—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts

Definitions

  • the invention relates to gear sets for converting torque and speed of a source of rotational power, and in particular to gear sets having multiple lay shafts for load sharing.
  • To reduce the size and mass of a gear box it is known to transmit the load through multiple intermediate shafts (also known as lay- or countershafts) rather than one larger lay shaft.
  • This allows for a reduction in the overall size of the gear box, because loads can be transmitted more effectively over two smaller shafts rather than one larger shaft.
  • Imperfections in the gears can cause one gear to engage before the others, leading to a larger proportion of the load being taken on a single lay shaft. This results in the lay shafts having to be engineered with increased safety factors, reducing the benefit of using such multiple shafts.
  • the illustrated gear set 100 provides for a reduction in speed between a drive shaft 19 and a driven shaft 11 , and a consequent increase in torque.
  • a pair of helical gears 22, 23 having equal and opposite helix angles drive two lay shafts 26, 28 through helical gears 24, 25 mounted on the lay shafts 26, 28.
  • the lay shafts 26, 28 engage with the driven shaft 19 through helical gears 32, 34, both of which mesh with an output helical gear 33.
  • the proportion of the load taken by each shaft 26, 28 can be controlled by altering the helix angles of each gear set 22, 24 and 23, 25. Equal load sharing is obtained by using equal helix angles of opposite hand. Because the load between the drive shaft 19 and the driven shaft 11 is shared between the lay shafts 26, 28, the overall size of the gear set can be reduced compared with a comparably rated gear set having only one lay shaft.
  • a gear set comprising: an input shaft;
  • each pair of gears being fixed relative to each other, axially moveable in tandem and mounted on the input or the output shaft;
  • gear set is configured such that an imbalance in load sharing between the lay shafts results in axial movement of the pairs of helical gears tending to reduce the imbalance.
  • a first pair of the two or more pairs of helical gears may be mounted on the input shaft and a second pair mounted on the output shaft, each of the input gears of the three or more lay shafts being engaged with only one of the first pair of helical gears, each of the output gears of the three or more lay shafts being engaged with only one gear of the second pair of helical gears.
  • the three or more lay shafts may comprise:
  • first lay shaft having an input gear engaged with a first one of the first pair of helical gears and an output gear engaged with a first one of the second pair of helical gears;
  • second lay shaft having an input gear engaged with the first one of the first pair of helical gears and an output gear engaged with a second one of the second pair of helical gears;
  • a third lay shaft having an input gear engaged with a second one of the first pair of helical gears and an output gear engaged with the second one of the second pair of helical gears.
  • the gear set may comprise a third pair of helical gears, the third pair being mounted on the output shaft, wherein the three or more lay shafts comprise:
  • a first lay shaft having an input gear engaged with a first one of the first pair of helical gears and an output gear engaged with a first one of the second pair of helical gears;
  • a second lay shaft having an input gear engaged with a second one of the first pair of helical gears and an output gear engaged with a first one of the third pair of helical gears;
  • a third lay shaft having an input gear engaged with the first one of the first pair of helical gears and an output gear engaged with a second one of the second pair of helical gears;
  • a fourth lay shaft having an input gear engaged with the second one of the first pair of helical gears and an output gear engaged with a second one of the third pair of helical gears.
  • the gear set may comprise two or more pairs of helical gears mounted on the output shaft, each gear of the two or more pairs of helical gears being engaged with an output gear of a different lay shaft. This arrangement is particularly suitable for gear sets having even numbers of lay shafts.
  • the gear set may also or alternatively comprise two or more pairs of helical gears mounted on the input shaft, an input gear of each lay shaft being engaged with one of the gears of the two or more pairs of helical gears.
  • Each gear of the two or more pairs of helical input gears may be engaged with an input gear of a different lay shaft.
  • the gear set may be configured so as to share load substantially equally among the lay shafts. This is preferably achieved by the helix angles of the gears of the pairs of input and output helical gears being substantially equal. For some embodiments, for example when a first gear of a pair of helical gears engages with only one lay shaft gear while the second gear of the pair engages with two gears, to achieve equal load sharing a tangent of the helix angle of the first gear is preferably approximately twice a tangent of the helix angle of the second gear.
  • a first pair and a second pair of the two or more pairs of helical gears are mounted on the input shaft, an input gear of a first one of the lay shafts comprising a third pair of helical gears of opposite hand fixed relative to each other and axially moveable in tandem on the first lay shaft, the third pair of helical gears being engaged with respective gears of the first and second pairs of helical gears.
  • a second one of the lay shafts preferably has an input gear engaged with one of the gears of the second pair of helical gears
  • a third one of the lay shafts has an input gear engaged with one of the gears of the first pair of helical gears.
  • a fourth pair of helical gears may be mounted on the input shaft, with a fourth lay shaft having an input gear engaged with one of the gears of the fourth pair of helical gears, the input gear of the third lay shaft comprising a fifth pair of helical gears of opposite hand fixed relative to each other and axially moveable in tandem, the fifth pair of helical gears being engaged with respective gears of the second and fourth pairs of helical gears.
  • one or more of the lay shaft output gears may be axially adjustable so as to balance a load between the lay shafts. Such adjustments are preferably made during assembly prior to fixing the adjustable gear in place, for example by bolting or welding the gear to the lay shaft.
  • a particular advantage of the invention is that three or more lay shafts can be used in the gear set and the load between them can be shared according to how the pairs of helical input and output gears are arranged.
  • the gear set will be configured such that load sharing is equal between the lay shafts, by configuring the helical angles of the pairs of input and output gears, although other arrangements where the load is required to be shared in a different way between the lay shafts are possible through choice of the helical angles of the gears.
  • An aim of the invention is to allow a gear set with any number of lay shafts to obtain equal load sharing (or any other desired load sharing).
  • To obtain load sharing among the lay shafts at least one additional axially moveable gear pair is required. Load sharing is assured by ensuring that each lay shaft has a unique transmission path from the input shaft to the output shaft.
  • a first pair of the two or more pairs of helical gears consists of a pair of internal gears connected to the input shaft via an annular support shaft.
  • the use of internal, rather than external, gears on the input shaft allows for a higher gearing ratio while maintaining a compact size.
  • Axial movement of internal gears is preferably achieved by having the annular support shaft axially moveable relative to the input shaft, for example by means of a spline, although other means of allowing axial movement of internal gears may also be possible, for example by mounting the gears to allow axial movement relative to the annular shaft.
  • the lay shafts may each comprise a plurality of input gears engaged with different subsets of gears mounted on the input shaft.
  • the plurality of input gears on each lay shaft may optionally be engaged with all but one of the gears mounted on the input shaft.
  • Two of the lay shafts may be axially moveable relative to the input shaft and comprise three input gears engaged with corresponding gears mounted on the input shaft.
  • Two of the three gears of the two lay shafts may comprise a pair of helical gears fixed relative to each other and axially moveable in tandem engaged with a corresponding pair of helical gears mounted on the input shaft.
  • figure 1 is a cross-sectional drawing of a known gear set having two lay shafts
  • figure 2 is a schematic cross-sectional drawing of a gear set having three lay shafts
  • figure 3 is a schematic cross-sectional drawing of a gear set having four lay shafts;
  • figure 4 is a schematic diagram illustrating the power flow for the known gear set of figure 1 ;
  • figure 5 is a schematic power flow diagram illustrating an extension to the gear set of figure 4.
  • figure 6 is a schematic power flow diagram illustrating the embodiment show in figure 2;
  • figure 7 is a schematic power flow diagram illustrating an alternative embodiment having four lay shafts
  • figure 8 is a schematic power flow diagram illustrating an alternative embodiment having five lay shafts
  • figure 9 is a schematic power flow diagram illustrating a further alternative embodiment for three lay shafts.
  • figure 10 is a schematic diagram of an arrangement of pairs of helical gears used in the embodiment of figure 9;
  • figure 11 is a schematic power flow diagram of a further alternative embodiment for four lay shafts
  • figure 12 is a schematic power flow diagram of a further alternative embodiment for axial load cancellation and load sharing among four lay shafts;
  • figure 13 is a schematic power flow diagram of a further alternative embodiment for axial load cancellation and load sharing with two lay shafts;
  • figure 14 is a schematic power flow diagram of a further alternative embodiment for load sharing between four lay shafts
  • figure 15 is a schematic cross-sectional drawing of an alternative embodiment of a gear set having four lay shafts
  • figure 16 is a schematic power flow diagram of the input side of a modified arrangement of the gear set of figure 12;
  • figure 17 is a simplified schematic power flow diagram of the gear set of figure 16;
  • figure 18 is a schematic power flow diagram of a further modified arrangement of the gear set of figure 17;
  • figure 19 is a schematic power flow diagram of the input side of a modified arrangement of the gear set of figure 9;
  • figure 20 is a schematic power flow diagram of an alternative embodiment of a gear set having four lay shafts
  • figure 21 is a schematic cross-sectional drawing of an alternative embodiment of a gear set having three lay shafts; and figure 22 is a schematic cross-sectional drawing of a further alternative embodiment of a gear set having four lay shafts.
  • Figure 1 which illustrates a known gear set from US1759689, has already been described as part of the background to the invention above.
  • Shown in figure 2 is a gear set 200 having three lay shafts 207, 208, 209.
  • Each lay shaft has an input gear 204, 205, 206 engaged with one of a pair of input helical gears 202, 203 mounted on an input shaft 201.
  • the pair of helical input gears 202, 203 are configured to rotate with the input shaft 201.
  • the helical input gears 202, 203 are fixed relative to one another, for example by being formed as a single unit, but are mounted such that a degree of axial movement of the pair is allowed. This may be achieved by the helical input gears 202, 203 being slidable along the axis 221 of the input shaft 201, which is preferably coincident with the axis of the output shaft 215 of the gear set 200.
  • the lay shafts 207, 208, 209 each also have an output gear 210, 211, 212 engaged with one of a pair of helical output gears 213, 214.
  • the pair of helical output gears 213, 214 are, similarly to the pair of helical input gears 202, 203, configured such that they are fixed relative to one another but are axially moveable in tandem.
  • the pair of helical input gears 202, 203 ensures that load is shared appropriately between lay shaft 209 and lay shafts 207, 208, while the helical output gear pair 213, 214 ensures that load is shared between lay shaft 207 and lay shafts 208, 209.
  • the combination of the two axially moveable gear pairs 202, 203 and 213, 214 ensures the overall load is split between the three shafts 207, 208, 209.
  • the tangent of the helix angle of gear 202 should be twice the tangent of the helix angle of 203 and the tangent of the helix angle of 213 should be twice the tangent of the helix angle of 214.
  • each pair of helical gears will need to balance a load from two lay shafts with the load from one lay shaft.
  • the helix angle of a helical gear may be defined as being the angle between a tangent to the teeth of the gear and an axis about which the gear rotates. References herein to pairs of helical gears being of opposite hand mean that the helix angles of the gears are opposite in sign but not necessarily equal in magnitude.
  • the gear set 300 in figure 3 comprises lay shafts 302, 303, 304, 305 and three pairs of axially moveable helical gears 306, 307, 316, 317 and 318, 319.
  • a first pair of helical gears 306, 307 is mounted on the input shaft 301.
  • Each of the lay shafts 302, 303, 304, 305 have an input gear 308, 309, 310, 311 engaged with only one of the gears of the input helical gear pair 306, 307.
  • Each gear of the pair of helical input gears 306, 307 is engaged with input gears of two of the lay shafts, a first one 306 of the pair of helical input gears engaged with input gears 309, 311 of lay shafts 303, 305 and a second one 307 engaged with input gears 308, 310 of lay shafts 302, 304.
  • each one of the pairs of helical output gears 316, 317, 318, 319 is engaged with only one of the output gears 312, 313, 314, 315 of the lay shafts 302, 303, 304, 305.
  • the gears in each pair of helical gears are fixed relative to one another but are axially moveable in tandem.
  • equal load sharing can be achieved by having an equal helical angle on each of the pairs of helical input and output gears.
  • Load sharing between a first pair of lay shafts 302, 304 and a second pair of lay shafts 303, 305 is achieved by axial movement of the input pair of helical gears 306, 307.
  • Load sharing between lay shaft 303 and lay shaft 305 is achieved by axial movement of a first pair of helical output gears 316, 317.
  • Load sharing between lay shaft 302 and lay shaft 304 is achieved by axial movement of a second pair of helical output gears 318, 319.
  • the input load on the input shaft 301 is shared equally between the four lay shafts 302, 303,
  • gear sets 304, 305 As mentioned above, for equal load sharing an equal helix angle should preferably be chosen. However, other choices of helix angle can be chosen if a different degree of load sharing is required, for example to apply more load to one pair of lay shafts compared to the other by altering the helical angles of the input pair of gears 306, 307.
  • the use of the terms 'input' and 'output' to denote the relative positions of various gears in the gear sets described herein does not necessarily indicate that the arrangements described can only be used in the direction thereby implied.
  • the gear sets may alternatively be used in the reverse direction, i.e. where an input gear becomes an output gear and vice versa.
  • FIGs 4 to 7 are schematic power flow diagrams illustrating various possible arrangements using multiple lay shafts and different load sharing arrangements.
  • straight horizontal lines represent shafts
  • filled ellipses represent pairs of helical gears of opposite hand axially moveable in tandem on the relevant shaft, and restricted to rotate with the shaft on which they are mounted.
  • Filled rectangles represent normal gears, which for the purposes of load sharing can be considered to be constrained to rotate with the shafts they are mounted upon, as well as being axially fixed to that shaft.
  • figure 4 illustrates the gearing arrangement as disclosed in US1759689 and described above with reference to figure 1.
  • Vertical lines 401 , 402, extending between a pair of helical gears 403 on an input shaft 404 and corresponding input gears 405, 406 on lay shafts 407, 408, represent meshing of either gears 22, 24 or gears 23, 25 of figure 1.
  • Vertical lines 409, 410, extending between output gears 411 , 412 on lay shafts 407, 408 and an output gear 413 on output shaft 414, represent meshing of gears 32, 34 on lay shafts 26, 28 with output gear 33 on the output shaft 11.
  • the handedness of the gears 22, 23, 24, 25 is indicated according to whether a vertical line extends upwards or downwards from a gear, i.e. a right-handed gear is represented by a line travelling downwards from an ellipse and a left-handed gear by a line travelling upwards from an ellipse.
  • a vertical line extends upwards or downwards from a gear
  • a right-handed gear is represented by a line travelling downwards from an ellipse
  • a left-handed gear by a line travelling upwards from an ellipse.
  • Gears on the input shaft may be either external gears, as illustrated in figures 1 to 3, or may be internal gears, as illustrated in figure 15 (described in more detail below).
  • An external gear is defined by the gear teeth being on the outer surface of the gear, whereas an internal gear is defined by the gear teeth being on the inner surface.
  • the "handedness" (i.e. left handed or right handed) of an internal gear is opposite to that of an external gear that it replaces. The same replacement of internal gears for external gears may be performed on the output shaft, with the same requirement for reversing the handedness.
  • the diagram of figure 5 illustrates how the arrangement of US 1759689 can be extended to load sharing using four lay shafts 501 , 502, 503, 504, through the use of intermediate shafts 505, 506.
  • this can be extended to any even number of lay shafts, i.e. by adding further pairs of lay shafts to connect with one or more of the outermost lay shafts 501, 504 indicated in the diagram.
  • the four lay shaft output gears 507, 508, 509, 510 all mesh with a single gear 511 mounted on the output shaft 512.
  • a disadvantage with this approach is the need for additional intermediate lay shafts and gearing, which increases the size and cost of the gear set.
  • Figure 6 shows a gear set 600 having a three lay shaft load sharing arrangement corresponding to the embodiment illustrated in figure 2.
  • the input shaft 601 has a first pair of helical gears 602 mounted thereon, a first one of the first pair of helical gears 602 engaged with input gears 603, 604 of a first lay shaft 605 and a second lay shaft 606, while a second one of the first pair of helical gears 602 is engaged with an input gear of a third lay shaft 607.
  • An output gear 608 of the first lay shaft 605 is engaged with a first one of a second pair of helical gears 609 mounted on the output shaft 610, while output gears 611 , 612 of the second and third lay shafts 606, 607 are engaged with a second one of the second pair of helical gears 609.
  • Figure 7 shows a gear set 700 having a four lay shaft load sharing arrangement similar to the embodiment illustrated in figure 3.
  • FIG 7 differs from that shown in figure 3, in that the third lay shaft 703 is engaged with the same gear of the first pair of helical gears 706 as the first and second lay shafts 701, 702, while only the fourth lay shaft 704 is engaged with the other gear of the first pair of helical gears 706.
  • Figure 8 illustrates a gear set 800 in which load sharing is achieved among five lay shafts by adding a fifth lay shaft 805 to the four lay shafts 801 , 802, 803, 804 arranged similarly to those in figure 7, and a further pair of helical gears 807 on the input shaft 808.
  • the first lay shaft 801 instead of engaging with the pair of helical gears 806, engages with a first one of the further pair 807, while the fifth lay shaft 805 engages with a second one of the further pair 807.
  • This principle of adding further lay shafts and further pairs of helical gears can, in theory, be extended to any number of lay shafts. In practice, however, the number of lay shafts possible using this technique will be limited by the distance the lay shafts are offset from the input and output shafts, and by the greatest diameter of the tips of the gear teeth of the largest lay shafts. Beyond 32 parallel lay shafts the benefits are expected to be limited, as the input and output gears would have to be rather large relative to the lay shaft gears in order to achieve a useful ratio between the input and output shafts.
  • a practical upper limit on the number of lay shafts is therefore 32, with a typical arrangement having between 3 and 8 lay shafts.
  • the output gear sets on the right hand (or output) side of each of these diagrams have a handedness which is independent to the left hand (or input) side.
  • the handedness of the output gears can therefore be inverted, and load sharing among the lay shafts will be unaffected.
  • the relative location of gears on the input shaft and also on the output shaft is also not relevant, and will not affect the load sharing.
  • gears mounted on the output shaft need to be selectively engaged to the output shaft to provide a choice of ratios, for example by means of one or more synchronisers
  • the gear set 900 illustrated in figure 9 shows how this may be achieved for 3 lay shafts.
  • a first pair 901 and a second pair 902 of helical gears are mounted on the input shaft 903, while normal gearing 904 is mounted on the output shaft 905.
  • a third pair 906 of helical gears is mounted on the first lay shaft 907, the third pair 906 being engaged with one gear of both the first and second pairs 901 , 902.
  • Input gears 910, 911 of the second and third lay shafts 908, 909 are engaged with gears of the second and first pairs 902, 901 of helical gears with which the pair of helical gears 906 is not engaged.
  • Each of the pairs of helical gears 901 , 902, 906 are axially moveable on their respective shafts, allowing load sharing among the three lay shafts 907, 908, 909.
  • the arrangement of axially moveable pairs of helical gears shown in figure 9, and extended further in the gear set shown in figure 11 (described below), is characterised by the way in which only one gear on each axially moveable pair of helical gears is in mesh with a gear on another axially moveable gear pair.
  • This is illustrated in figure 10, in which a first, second and third pair of helical gears 1001 , 1002, 1003 are shown in mesh with each other.
  • the first and second pairs 1001 , 1002 are mounted, and axially moveable, on a first shaft 1004, while the third pair 1003 is mounted, and axially moveable, on a second shaft 1005.
  • Axial movement of each of the pairs 1001, 1002, 1003 of helical gears allows for load sharing between the second shaft 1005 and two other shafts having gears meshing with the first and second pairs 1001 , 1002.
  • the third pair 1003 of helical gears and the second shaft 1005 in figure 10 correspond with the third pair 906 of helical gears and the first lay shaft 907 in figure 9, while the first and second pairs 1001, 1002 of helical gears in figure 10 correspond with the first and second pairs 901 , 902 of helical gears in figure 9.
  • the gear set 1100 shown in figure 11 shows that, by adding another two axially moveable pairs of helical gears 1111 , 1112, load can be shared over a fourth lay shaft 1110 in addition to the first, second and third lay shafts 1107, 1108, 1109. This change from 3 to 4 lay shafts can be iterated further when adding more lay shafts.
  • all of the axially moveable pairs of gears 901 , 902, 1101, 1102, 1112 on the input shaft 903, 1103 are driven directly by the input shaft 903, 1103. This means that, for equal load sharing on all the lay shafts, the gears on the input shaft which mesh with just one gear on a lay shaft (i.e.
  • the gears of pairs 901 , 902 which mesh with gears on pair 906, and the gears of pairs 1101 , 1102, 1112 which mesh with gears on pairs 1106 and 1111) will preferably need approximately twice the face width to have an equivalent strength, and will preferably have a helix angle with a tangent about double that of all the other driving gears on the input shaft to allow for equal load sharing.
  • the driven and driving gears must be of the same hand.
  • any lay shaft having input and output gears engaged with respective gears of pairs of helical gears is engaged with gears having the same hand.
  • FIG 13 An alternative embodiment of a gear set in which axial loading may be minimised or cancelled is shown in figure 13.
  • this gear set 1300 two non-axially moveable gears 1301 , 1302 mounted on the same lay shaft 1303 are used, instead of on two different lay shafts.
  • this can be extended to include further lay shafts, but in this case maintaining cancellation of axial loading.
  • This alternative embodiment is able to achieve both equal load sharing and zero axial loading on all shafts for an odd number of lay shafts. For equal load sharing on the lay shafts in this case, all the helix angles of the input gears should be the same.
  • the output gears can either have zero helix angle (i.e. spur gears) or that they are of a herringbone nature (pairs of rigidly connected helix gears of opposite hand) and those gears mounted on the lay shafts are axially moveable to ensure that both flanks of opposite hand on the herringbone gear share the load equally.
  • the benefit of more than 32 parallel shafts is expected to become less effective, for the same ratio limiting reasons described above in relation to the other embodiments.
  • Shown in figure 14 is a schematic power flow diagram for a further alternative embodiment of a gear set 1400 having four lay shafts 1404, 1405, 1406, 1407, in which load sharing between a first pair of lay shafts 1404, 1407 is achieved by means of a first pair of helical gears 1401 on the input shaft 1403 and load sharing between a second pair of lay shafts 1405, 1406 is achieved by means of a second pair of helical gears 1402 on the input shaft 1403.
  • This particular embodiment, in which the output gear 1408 is axially fixed on the output shaft 1409, is particularly suitable where the output gear is required to be large, for example in wind turbine applications, or where multiple gearing ratios are to be selected, such as in automotive applications. In both of the situations, axially movable pairs of output gears are either less practical or infeasible.
  • Such an adjustment can be done for example by measuring a torque on the lay shafts and adjusting the axial position of one of the gears 1410, 1411 , 1412, 1413 until the torque is equal to the desired proportion of the input torque (which, in this case, will preferably be one quarter of the input torque).
  • the gear can then be fixed in position, for example by bolting, welding or otherwise permanently fixing the gear in place on the lay shaft.
  • the principle of allowing one or more of the output gears on the lay shafts to be axially adjustable can be extended to embodiments where more than four lay shafts are used and where the output gearing 1408 is fixed.
  • more than one of the output gears on the lay shafts can be made adjustable axially on assembly, to allow for the torque taken by each lay shaft to be balanced during an initial set up of the gear set.
  • the general principle to be applied is that the number of adjustable output gears will need to be equal or greater than the number of pairs of axially movable helical gears minus one.
  • the above principle can also be applied for applications where more than one gearing ratio can be selected on the output shaft.
  • an output gear on each lay shaft will be engaged with two or more gears on the output shaft, each output gear being selectably engaged with the output shaft, for example by means of a synchroniser.
  • the adjustment step for the one or more lay shaft output gears can be done for each output gear, the set up procedure involving an adjustment being made, followed by permanent fixing of the output gear, for each available gearing ratio.
  • Figure 15 shows an additional embodiment with four lay shafts.
  • the gear set 1500 comprises four lay shafts 1503, 1504, 1505, 1506 and three pairs of axially moveable helical gears 1507, 1508, 1517, 1518, 1519, 1520.
  • a first pair of internal helical gears, 1507, 1508 is housed in an annular support shaft, 1502.
  • the annular support shaft 1502 and the input shaft 1501 are connected by a coupling 1522 such that they are constrained to rotate together but free to move axially relative to each other, allowing the internal gears 1507 and 1508 to move axially in tandem.
  • Each of the lay shafts 1503, 1504, 1505, 1506 have an input gear 1509, 1510, 1511 , 1512 engaged with only one of the input helical gear pair 1507, 1508.
  • Each gear of the pair 1507, 1508 is engaged with input gears of two of the lay shafts, a first one 1507 engaged with input gears 1510, 1512 of lay shafts 1504, 1506 and a second one 1508 engaged with input gears 1509, 1511 of lay shafts 1503, 1505.
  • Each of the lay shafts 1503, 1504, 1505, 1506 also has an output gear 1513, 1514, 1515, 1516 engaged with only one gear of the two pairs of helical output gears 1517, 1518 & 1519, 1520 mounted on the output shaft 1521.
  • Each gear of the helical pairs 1517, 1518, 1519, 1520 is engaged with only one of the output gears 1513, 1515, 1514, 1516 respectively.
  • the coupling 1522 between the input shaft 1501 and the annular support shaft 1502 supporting the pair of helical input gears 1507, 1508 is preferably in the form of a spline.
  • the spline preferably has a clearance fit, so as to allow axial movement of annular support shaft 1502 relative to the input shaft 1501 while transmitting torque from input shaft 1501 to the annular support shaft 1502.
  • the axial positions of the input shaft 1501 and output shaft 1521 , and the bearing support arrangement for the four lay shafts 1503, 1504, 1505, 1506, would be fixed by their location in the transmission housing (not shown).
  • a greater load capacity can be gained by adding further lay shaft gears.
  • An input or output arrangement of gear sets can be replaced with the same number of gear sets, but with a greater number of lay shaft gears, by adding, on each lay shaft, a pair of gears of equal helix angle and opposite hand constrained to move axially in tandem and constrained to rotate with the lay shaft upon which they are mounted. These additional pairs of tandem lay shaft gears mesh with any axially moveable tandem gear pair mounted on the input or output shaft.
  • Figure 16 shows a modified arrangement for the input half of the gear set of figure 12.
  • the arrangement in figure 16 can be derived from the schematic diagram in figure 12 in the following way. Firstly, all gears mounted in any way on the input shaft are unchanged. Secondly, each lay shaft input gear is replaced by a collection of gears which mesh with all the gears on the input shaft with the exception of the lay shaft gear (or gears) being replaced. The same process is then repeated for the output shaft.
  • Figure 16 is a substantially more complicated diagram as a result, as there are 3 times as many lay shaft input gears, and therefore 3 times as many meshing connections to show.
  • the lay shafts 1604, 1605, 1606, 1607 each comprise a plurality of input gears engaged with different subsets of gears 1601 , 1602, 1608 (or 1701 , 1702, 1708) mounted on the input shaft 1603 (or 1703).
  • the plurality of input gears on each lay shaft are in this case engaged with all but one of the gears 1601 , 1602, 1608 (or 1701 , 1702, 1708) mounted on the input shaft 1603 (or 1703), although in other embodiments more than one gear on the input shaft may be disengaged from each lay shaft.
  • the original drawing convention for handedness is modifed accordingly.
  • the axially moveable gear pairs on the lay shafts will tend to centre themselves to carry an equal load through each half, provided they have equal helix angles.
  • the collection of input or output gears that replaces the input or output gear on the lay shaft will need to be manufactured and assembled with low clocking angle errors between the gears for load sharing between shafts to be successful. Different clocking angle errors between different lay shafts are not a problem, as this is adjusted for as if there were only one input gear on each lay shaft.
  • the transmission 1200 of figure 12 has the feature of being able to balance the axial forces on all the shafts, which has the benefit of minimising bearing loads.
  • the embodiments of figures 17, 18 and 22 are derived from transmission 1200 as outlined above, and also benefit from this feature.
  • an empty square is used to indicate where a gear is not present to mesh with a particular gear on the input or output shaft and the presence of a gear to mesh with all the other gears on the same input or output shaft is implied.
  • a black circle represents 2 gears of opposite hand
  • an empty square with a single connecting line to a circle implies the absence of a single gear connecting to the indicated single hand of the 2 pairs of gears.
  • Figures 17 and 22 show the same transmission arrangement 1700, with figure 17 being a schematic diagram of the transmission layout drawn in figure 22.
  • the transmission 1700 of figures 17 and 22 is equivalent to that shown in figure 16, but with the addition of an output section which is the same as it appeared in figure 12.
  • Lay shaft 1704 has three input gears, two of which mesh with both halves of the helical gear pair 1708, the other with gear 1702 but not with 1701.
  • lay shaft 1706 has three gears, two of which mesh with both halves of the helical gear pair 1708 and the other with gear 1701 but not with gear 1702.
  • lay shafts 1704, 1706 For both these lay shafts 1704, 1706, the two gears which mesh with both halves of input gear pair 1708 are of opposite hand, are axially moveable in tandem upon the lay shaft, but are constrained to rotate with the lay shaft upon which they are mounted.
  • input shaft gears 1701, 1702 would be adjacent, and not separated by the gear pair 1708.
  • these lay shafts 1705 and 1707 both have an axially fixed gear which meshes with the opposite hands of input gear pair 1708.
  • the axially fixed input gear on lay shaft 1705 has the opposite hand to the axially fixed input gear on lay shaft 1205 in transmission 1200.
  • the axially fixed input gear on lay shaft 1707 has the opposite hand to the axially fixed input gear on lay shaft 1207 in transmission 1200.
  • lay shafts 1804, 1806 the two gears which mesh with both halves of input gear pair 1808 are of opposite hand and are axially moveable in tandem upon the lay shaft, but are constrained to rotate with the lay shaft upon which they are mounted.
  • Lay shafts 1805 and 1807 each have a pair of gears of opposite hand axially moveable in tandem, which mesh with input shaft gears 1801 and 1802.
  • these lay shafts 1805 and 1807 both have an axially fixed gear which meshes with the opposite hands of input gear pair 1808.
  • Lay shaft 1804 also has three output gears, a pair of which mesh with both gear halves of helical gear pair1809 but only one of the gear halves of gear pair 1811.
  • Lay shaft 1805 has three output gears, a pair of which mesh with both gear halves of helical gear pair 1811 but only one of the gear halves of gear pair 1809.
  • Lay shaft 1806 has three output gears, a pair of which mesh with both gear halves of helical gear pair 1811 but only one of the gears of gear pair 1809.
  • Lay shaft 1807 has three output gears, a pair of which mesh with both gear halves of helical gear pair 1809 but only one of the gears of gear pair 1811.
  • the axially moveable gear pair 1809 is meshed with gears on lay shafts 1805 and 1806, which have opposite hands.
  • the moveable gear pair 1811 is meshed with gears, on lay shafts 1804 and 1807, which have opposite hands.
  • the two lay shaft ouput gears that form a pair are axially moveable in tandem, but constrained to rotate with the lay shaft upon which they are mounted.
  • the feature of dynamic adjustment of the axial position of the gear pairs when selecting and engaging a gear can also be used with this method.
  • the number of lay shafts that could be adjusted for in the inventive manner will be limited by the increasing frictional forces that will be encountered when axially moving a tandem gear pair on the input shaft, which is also meshed with a axially moveable gear pair on another lay shaft, as this other gear pair would also have to move at the same time.
  • lay shafts axially moveable tandem gear pairs are to be mounted on a spline to allow the axial movement but the transmission of torque
  • all the input gears for a lay shaft should have the spline cut simultaneously in a single operation, and at assembly, the immobile gear which has no pair, axially fixed in place.
  • This axial fixing location could be quickly selected by meshing all the gears with a master input shaft, which has been adjusted for minimum clocking angle error.
  • lay shaft 1907 still has an axially moveable in tandem gear pair 1906 of opposite hand, however, this now meshes with gears 1901 and 1902 with opposite hand than in the previous transmission 900.
  • Lay shafts 1908 and 1909 now have three input gears each.
  • Lay shaft 1908 has an axially moveable tandem gear pair which meshes with axially moveable tandem gear pair 1901 on the input shaft 1903.
  • Lay shaft 1908 also has an axially fixed input gear which meshes with one half of the axially moveable gear pair 1902 on the input shaft, and the half with which it meshes is opposite to the half to which lay shaft 1907 has a gear 1906 in mesh with 1902.
  • lay shaft 1909 has an axially moveable tandem gear pair which meshes with axially moveable tandem gear pair 1902 on the input shaft 1903.
  • Lay shaft 1909 also has an axially fixed input gear which meshes with one half of the axially moveable gear pair 1901 on the input shaft, and the half with which it meshes is opposite to the half to which lay shaft 1907 has a gear 1906 in mesh with 1901.
  • the shortest input set length can be achieved by choice of helix angles where the ratio of the tangents of the helix angles is two.
  • the halves of gear pairs 1901 and 1902 that are in mesh with gear pair 1906 will then each transmit a third of the input torque, and the halves that are not in mesh with gear pair 1906 will transmit one sixth of the input torque. If the input gear transmitting a sixth of the input torque has twice the helix angle of the gears transmitting one third of the input torque, then each lay shaft will receive a third of the total input torque.
  • Any lay shaft gear meshed with either of the input gear halves that mesh with the tandem gear pair 1906 on the lay shaft 1907, will carry half the torque for that lay shaft. It follows that the input gears on the lay shafts can be sized for the load capacity that matches the torque distribution amongst that lay shafts input gears
  • the requirements for minimising the clocking angle difference between lay shaft input gears can be avoided by using only a single output helical gear on each lay shaft, and having a maximum of one axially moveable tandem gear pair in addition to the axially fixed helical gear as lay shaft input gears.
  • the unpaired lay shaft input gear and the lay shaft output gear are designed to balance their axial forces, when the unpaired input gear is receiving the designed torque in proportion to the total torque transmitted by that lay shaft. Allowing the axial movement of that lay shaft will then mean any imbalance in the proportion of the torque received by the unpaired lay shaft input gear will cause an axial movement of the lay shaft to reduce that imbalance.
  • the embodiments in transmissions 2000 and 2100 illustrated in figures 20 and 21 use this principal to improve the load carrying capacity of their input gears.
  • Figure 20 shows a schematic diagram of transmission 2000, which is suitable for a fixed high ratio application.
  • Input shaft 2003 rotates the input gears 2001 , 2002 and the axially moveable in tandem gear pair of opposite hand, 2008.
  • Input gears 2001 and 2002 are of opposite hand, but have no need to be axially moveable either individually, or in tandem.
  • input gears 2001 , 2002, 2008 all have the same helix angle.
  • Lay shafts 2004, 2005, 2006 and 2007 each have three input gears. Of the three input gears on each of these lay shafts 2004, 2005, 2006, 2007, two of these input gears form an axially moveable tandem gear pair of opposite hand.
  • Lay shaft 2004 has a tandem gear pair which meshes with both halves of tandem gear pair 2008 on the input shaft, and the remaining input gear on lay shaft 2004 meshes with gear 2002 on the input shaft 2003.
  • Lay shaft 2005 has an axially moveable tandem gear pair of opposite hands, which meshes with gears 2001 and 2002 on the input shaft, and the remaining input gear meshes with one half of the tandem gear pair 2008 on the input shaft 2003.
  • Lay shaft 2006 has a tandem gear pair which meshes with both halves of tandem gear pair 2008 on the input shaft, and the remaining input gear on lay shaft 2006 meshes with gear 2001 on the input shaft 2003.
  • Lay shaft 2007 has an axially moveable tandem gear pair of opposite hands, which meshes with gears 2001 and 2002 on the input shaft, and the remaining input gear meshes with one half of the tandem gear pair 2008 on the input shaft 2003.
  • all four lay shafts 2004, 2005, 2006, 2007 are designed to carry the same torque, and for each of those lay shafts, their three input gears are designed to carry about one third of the torque for that lay shaft.
  • the ratio of the tangents of the helix angles of output gears 2009, 2011 to the input gears 2001 , 2002, 2008 is chosen to balance the axial force caused by the one third of the lay shaft torque on the unpaired gear being driven at its average operating diameter, with the whole of the lay shaft torque driving the lay shaft output gear at the lay shaft output gears average operating diameter, in mesh with either of 2011 or 2009.
  • the axially moveable tandem gear halves of 2009 and 2011 therefore have the same helix angle. If the unpaired lay shaft input gear is carrying more than one third of the torque on that lay shaft, the lay shaft output gear will not be able to oppose the extra axial force generated, and that lay shaft will slide axially.
  • lay shaft's axially moveable tandem gear pair will stay in its original axial position.
  • the relative movement of the unpaired lay shaft input gear relative to the axially moveable tandem gear pair will improve the load sharing over those input gears. If the unpaired lay shaft input gear were to carry less than one third of the lay shaft torque, the lay shaft would move in the opposite direction, and again improve the load sharing.
  • the average operating diameter is the average of the start of the active profile and the end of the active profile, and is frequently approximately equal to the working pitch diameter.
  • the ratio of the tangent of the helix angles measured at their respective average operating diameters is the relevant helix angle. If the leads of the lay shaft input and output gears are different an adjustment of one lay shafts axial position will require an additional movement of at least some of the input and output shafts axially moveable tandem gear pairs, to rebalance the torque through the different lay shafts. Therefore, in preferred embodiments the difference between the leads of the lay shafts input and output gears will be minimised.
  • Transmission 2000 also has intermediate shafts 2013, 2014 which are constrained to rotate with paired gears 2011 and 2009 respectively.
  • Intermediate shafts 2013 and 2014 have output gears 2016, 2017, which drive output shaft 2012 via output gear 2015.
  • 2015 is a double helical or herringbone gear of equal helix angle and opposite hand
  • the gears 2016 and 2017 are both pairs of helical gears of equal helix angle and opposite hand, free to move axially relative to the output gear 2015.
  • Figure 2100 illustrates part of a transmission 2100 in which the input shaft 2103 drives three lay shafts 2107, 2108, 2109 which in turn drive output shaft 2105.
  • This transmission 2100 could be extended to allow multiple gearing ratios to be selected by duplicating the output gear set which is comprised of output shaft gear 2104, and lay shaft gears 2110, 2111 , 2112 that are simultaneously drivingly engaged with output shaft gear 2104.
  • the duplicated set would have differing numbers of gear teeth to the original output gear set, and either or neither of the original gear set or the duplicated set could be engaged driving. When neither gear set is engaged, it would be possible to engage one of further duplicated gear sets with differing ratios.
  • Input shaft 2103 has four gears 2117, 2118 and 2119, 2120 connected by couplings 2123, 2122 to the input shaft 2103.
  • the lay shafts are designed to transmit equal torque.
  • Input gears 2117 and 2120 have the same helix angle, and input gears 2118, 2119 have the same helix angle.
  • the tangent of the helix angle of input gear 2117 is approximately half the tangent of the helix angle of input gear 2118, and they are of opposite hand, and constrained to rotate with the input shaft 2103 but free to move axially in tandem.
  • the difference in helix angles means that input gear 2117 will transmit twice the torque of input gear 2118, and the input gear face widths, and the face widths of the gears that mesh with them can be different accordingly.
  • input gears 2119 and 2120 are of opposite hand, and are constrained to rotate with the input shaft 2103 but free to move axially in tandem, and input gear 2120 will also transmit twice the torque of input gear 2119.
  • Lay shaft 2108 has three input gears 2114, 2125, 2126 which are all constrained to rotate with it; gear 2114 is also constrained to move axially with the lay shaft 2108, but gears 2125 and 2126 are free to move axially in tandem and are connected to the lay shaft by coupling 2124.
  • lay shaft 2109 has 3 input gears 2115, 2127, 2128 which are all constrained to rotate with it; gear 2115 is also constrained to move axially with the lay shaft 2109, but gears 2127 and 2128 are free to move axially in tandem and are connected to the lay shaft by coupling 2121.
  • Input gear 2117 is engaged with lay shaft gears 2113 and 2125; input gear 2118 is engaged with lay shaft gears 2115, 2126; input gear 2119 is engaged with lay shaft gears 2114, 2127; and input gear 2120 is engaged with lay shaft gears 2116, 2128.
  • Lay shaft gears 2125 and 2126 necessarily have opposite hand but equal helix angles to the input shaft gears with which they each mesh, and therefore will be axially balanced when gear 2125 is receiving twice the torque of gear 2126.
  • lay shaft gears 2127 and 2128 necessarily have opposite hand but equal helix angles to the input shaft gears with which they each mesh, and therefore will be axially balanced when gear 2128 is receiving twice the torque of gear 2127. Since paired gears 2125, 2126 and 2127, 2128 transmit no overall axial force, they do not affect the load sharing between lay shafts allowed for by the axial movement of input gears 2117, 2118 and 2119, 2120.
  • lay shaft 2107 has two input gears of the same hand, 2113 and 2116, and an output gear 2110 of opposite hand to the input gears 2113 and 2116. Lay shaft 2107 will therefore always generate an axial force when transmitting torque.
  • Lay shaft 2107 is prevented from moving in an axial direction, but lay shafts 2108 and
  • Gear 2114 is designed to receive one quarter of the torque of lay shaft 2108. This gear 2114 will generate an axial force proportional to the torque it actually receives when driven at its average operating diameter. This axial force is opposed by the axial force generated by gear 2111 driving the output shaft gear 2104 with the full torque of lay shaft 2108, at the average operating diameter of gear 2111.
  • the ratio of the helix angle tangents of gears 2111 and 2114 is therefore selected to have zero or near zero overall axial force when gear 2114 receives 25% of the torque of lay shaft 2108.
  • gear 2115 is designed to receive one quarter of the torque of lay shaft 2109. This gear 2115 will generate an axial force proportional to the torque it actually receives when driven at its average operating diameter. This axial force is opposed by the axial force generated by gear 2112 driving the output shaft gear 2104 with the full torque of lay shaft 2109, at the average operating diameter of gear 2112.
  • the ratio of the helix angle tangents of gears 2112 and 2115 is therefore selected to have zero or near zero overall axial force when gear 2115 receives 25% of the torque of lay shaft 2109. Since gears 2111 and 2112 have the same helix angle, so too will gears 2114 and 2115.
  • the axial mobility and the transmission of torque by couplings 2121 , 2122, 2123, 2124, may be satisfied by the use of a clearance spline, which in the case of transmissions subject to regular changing of gearing ratio such as an automotive gearbox, the clearance splines may benefit from lubrication to reduce the possibility of damage to the spline surfaces.
  • two lay shafts 2108, 2109 comprise three input gears 2114, 2125, 2126, 2115,
  • the two lay shafts 2108, 2109 are axially moveable relative to the input shaft 2103.
  • Two of the three gears of the two lay shafts 2108, 2109 comprise a pair of helical gears 2125, 2126, 2127, 2128 fixed relative to each other and axially moveable in tandem engaged with a coresponding pair of helical gears 2117, 2118, 2119, 2120 mounted on the input shaft 2103.
  • the two lay shafts are preferably configured to be axially moveable during use, so the lay shafts can change position when a different gear is selected, thereby cancelling axial forces on the lay shafts between the input and output gears.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear Transmission (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L’invention concerne un train d'engrenages (200) comprenant: un arbre d'entrée (201); un arbre de sortie (215); au moins deux paires roues hélicoïdales (202, 203, 213, 214) de sens opposé. Les roues de chaque paire sont fixées l'une relativement à l'autre, se déplacent en tandem dans le sens axial et sont montées sur l'arbre d'entrée ou l'arbre de sortie. Le train d'engrenages comprend également: au moins trois arbres intermédiaires (207, 208, 209) comportant chacun une roue d'entrée (204, 205, 206) en prise avec une des paires de roues hélicoïdales (202, 203), et une roue de sortie (210, 211, 212) en prise avec une roue (213, 214) disposée sur l'arbre de sortie (215) pour transmettre un mouvement de rotation de l'arbre d'entrée (201) à l'arbre de sortie (215). Le train d'engrenages (200) est conçu de telle sorte qu'un déséquilibre dans la répartition de la charge entre les arbres intermédiaires (207, 208, 209) entraîne un déplacement axial des paires de roues hélicoïdales (202, 203, 213, 214) tendant à réduire ce déséquilibre.
PCT/GB2010/001284 2009-07-03 2010-07-02 Train d'engrenages WO2011001155A2 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
GB1121893.0A GB2485290B (en) 2009-07-03 2010-07-02 Gear set
CN201080029896.6A CN102667237B (zh) 2009-07-03 2010-07-02 齿轮组

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0911506.4 2009-07-03
GB0911506A GB2471512A (en) 2009-07-03 2009-07-03 Gear set with helical gears which move axially to reduce imbalanced loads

Publications (3)

Publication Number Publication Date
WO2011001155A2 true WO2011001155A2 (fr) 2011-01-06
WO2011001155A8 WO2011001155A8 (fr) 2012-02-16
WO2011001155A3 WO2011001155A3 (fr) 2012-04-19

Family

ID=41008646

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2010/001284 WO2011001155A2 (fr) 2009-07-03 2010-07-02 Train d'engrenages

Country Status (3)

Country Link
CN (1) CN102667237B (fr)
GB (2) GB2471512A (fr)
WO (1) WO2011001155A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2884100A1 (fr) * 2013-12-16 2015-06-17 Areva Wind GmbH Engrenage planétaire, générateur éolien comprenant un engrenage planétaire et utilisation d'un engrenage planétaire

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3026452B1 (fr) * 2014-09-30 2016-10-28 Hispano Suiza Sa Reducteur de vitesse a deux lignes intermediaires de transmission
US11118535B2 (en) * 2019-03-05 2021-09-14 General Electric Company Reversing gear assembly for a turbo machine

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1759689A (en) 1927-08-06 1930-05-20 Falk Corp Gear set

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1273556A (en) * 1916-11-06 1918-07-23 Fore River Ship Building Corp Gearing.
US1459964A (en) * 1919-04-05 1923-06-26 Alquist Karl Gearing
US1740756A (en) * 1926-10-26 1929-12-24 Deutsche Schiff & Maschb Ag Power-transmission gear
GB814905A (en) * 1956-07-10 1959-06-17 Hindmarch Thomas Improved power transmission gear
US2982144A (en) * 1958-04-21 1961-05-02 Wallgren August Gunn Ferdinand Gearing
US3088334A (en) * 1960-11-17 1963-05-07 Falk Corp Multiple reduction gear unit
DE2940323C2 (de) * 1979-10-04 1983-12-29 BHS-Bayerische Berg-, Hütten- und Salzwerke AG, 8000 München Doppelschrägverzahntes, zweistufiges Stirnrädergetriebe
US4709590A (en) * 1986-06-11 1987-12-01 Eaton Corporation Herringbone geared multiple load sharing countershaft transmission
US5927147A (en) * 1998-02-09 1999-07-27 Harrier Technologies, Inc. Power sharing gear sets
US6334368B1 (en) * 2000-05-17 2002-01-01 Harrier Technologies, Inc. Multi-path gear sets with load sharing between paths

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1759689A (en) 1927-08-06 1930-05-20 Falk Corp Gear set

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2884100A1 (fr) * 2013-12-16 2015-06-17 Areva Wind GmbH Engrenage planétaire, générateur éolien comprenant un engrenage planétaire et utilisation d'un engrenage planétaire
WO2015091406A1 (fr) * 2013-12-16 2015-06-25 Areva Wind Gmbh Engrenage planétaire, générateur éolien comprenant un engrenage planétaire et utilisation d'un engrenage planétaire
JP2017503125A (ja) * 2013-12-16 2017-01-26 アレバ ウインド ゲーエムベーハー 遊星歯車装置、遊星歯車装置を備える風力発電機、および遊星歯車装置の使用法
KR101775300B1 (ko) * 2013-12-16 2017-09-05 아레파 빈트 게엠베하 플래너터리 기어, 플래너터리 기어를 포함하는 풍력 발전기 및 플래너터리 기어의 사용

Also Published As

Publication number Publication date
WO2011001155A8 (fr) 2012-02-16
GB2471512A (en) 2011-01-05
CN102667237B (zh) 2015-04-15
GB2485290A (en) 2012-05-09
GB201121893D0 (en) 2012-02-01
GB2485290B (en) 2016-04-20
WO2011001155A3 (fr) 2012-04-19
CN102667237A (zh) 2012-09-12
GB0911506D0 (en) 2009-08-12

Similar Documents

Publication Publication Date Title
US5528960A (en) Power transmission apparatus
CN102187120B (zh) 具有载荷分配系统的变速器
RU2600414C2 (ru) Планетарный механизм и соответствующий способ производства
US6364611B1 (en) Helicopter power transmitting apparatus
US20090320643A1 (en) Composite wave gear drive
CN103256343A (zh) 具有中间轴轴向移动的变速器
CN109923335B (zh) 用于具有行星齿轮系的减速单元的行星架
CN111734792B (zh) 工程机械动力换挡变速箱
JP2011518994A (ja) トランスミッション、とりわけデュアルクラッチトランスミッション
US4287790A (en) High-speed bevel gear transmission system
JP5319563B2 (ja) 切り替え可能な高荷重変速機
US5310391A (en) Compound planetary gear transmission having load equalization means
WO2011001155A2 (fr) Train d'engrenages
US6334368B1 (en) Multi-path gear sets with load sharing between paths
CN103453085A (zh) 齿轮箱装置
GB2071263A (en) Twin screw extruder with power branching gearing
US6746356B2 (en) Geared transmissions
JP2017044246A (ja) 波動歯車伝達装置
CN107406147A (zh) 具有两条中间传动线路的减速器
JP5989891B2 (ja) フローティング歯車多段変速機
EP3265696B1 (fr) Train d'engrenages planétaires comprenant des engrenages d'angle et un dispositif d'équilibrage de force
Majumdar et al. Design and Analysis of six speed gear box
EP2137431B1 (fr) Boîte de vitesse de véhicule motorisé et véhicule la comprenant
WO2011072601A1 (fr) Système d'entraînement par pignons ayant un partage de charge
CN103438159A (zh) 一种双离合自动变速器

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 201080029896.6

Country of ref document: CN

ENP Entry into the national phase in:

Ref document number: 1121893

Country of ref document: GB

Kind code of ref document: A

Free format text: PCT FILING DATE = 20100702

WWE Wipo information: entry into national phase

Ref document number: 1121893.0

Country of ref document: GB

WWE Wipo information: entry into national phase

Ref document number: 2821/MUMNP/2011

Country of ref document: IN

NENP Non-entry into the national phase in:

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 10793677

Country of ref document: EP

Kind code of ref document: A2